Hermetic compressor

ABSTRACT

In a stopper, by providing, in a position corresponding to a movable end vicinity of a discharge reed, a first regulation part having a predetermined clearance from the movable end vicinity of the discharge reed, since a hermetic compressor has such a two-stage spring characteristic that, until the movable end vicinity of the discharge reed touches the first regulation part, a spring characteristic is weak and, after the touch, the spring characteristic is strong, and there is obtained a discharge valve device which is easy to open and whose closing speed is rapid, it is possible to improve a delay in closing.

TECHNICAL FIELD

The present invention relates to a discharge valve device of a hermeticcompressor used mainly in a refrigeration/cold-storage apparatus and thelike.

BACKGROUND ART

As a conventional hermetic compressor, there is, as disclosed inJapanese Patent Unexamined Publication No. 10-318146 for instance, onehaving possessed the discharge valve device in which there is contrivedto reduce a noise at an operation time, and an energy efficiency isimproved by reducing a loss at an opening/closing time of a dischargereed.

Hereunder, the above conventional hermetic compressor is explained whilereferring to the drawings. FIG. 13 is a sectional view of theconventional hermetic compressor, and FIG. 14 is a plan view of theconventional hermetic compressor. Further, FIG. 15 is an exploded viewof the conventional hermetic compressor, FIG. 16 is a side sectionalview of a discharge valve device of the conventional hermeticcompressor, and FIG. 17 is a spring characteristic diagram of theconventional discharge valve device.

In FIG. 13, FIG. 14, FIG. 15, FIG. 16 and FIG. 17, hermetic container401 possesses discharge pipe 402 and suction pipe 403, which areconnected to a cooling system (not shown in the drawing). In a bottompart, oil 404 is stored, and motor element 407, which includes stator405 and rotor 406, and compression mechanism 408 driven by it areaccommodated, and an inside is filled with refrigerant 409.

Next, there is explained about a main constitution of compressionmechanism 408. Cylinder 410 possesses substantially cylindricalcompression chamber 411, and bearing part 412. Valve plate 413 possessesdischarge valve device 414 in a side reverse to cylinder 410, and closescompression chamber 411. Head 415 covers valve plate 413.

Suction muffler 416 is constituted from tail pipe 417 that is a suctionpassage of a refrigerant gas, which has been opened into hermeticcontainer 401, and a sound deadening space (not shown in the drawing),and the other end is communicated into compression chamber 411.

Crankshaft 418 has main shaft part 419 and eccentric part 420, and isshaft-supported to bearing part 412 of cylinder 410, and rotor 406 ispressing-in fixed. Piston 421 is inserted to cylinder 410 so as to becapable of reciprocating/sliding, and between it and eccentric part 420is connected by connecting rod 422.

Next, there is explained about discharge valve device 414 possessed incompression mechanism 408. In valve plate 413, there are provided, in aside reverse to cylinder 410, discharge hole 423 communicating withcylinder 410, and valve seat part 424 having been formed so as tosurround discharge hole 423. Discharge reed 425 consists of a leafspring material, and possesses opening/closing part 426 for opening andclosing valve seat part 424.

Head 415 possesses discharge chamber 427 accommodating discharge valvedevice 414, and monolithically forms stopper 428 regulating a degree ofopening of discharge reed 425. Valve plate 413, discharge reed 425 andhead 415 are disposed in this order, and monolithically connected tocylinder 410 side by bolt 429.

About the hermetic compressor having been constituted like the above,its operation is explained below. If electricity is supplied to motorelement 407, rotor 406 rotates, and crankshaft 418 is rotation-driven.At this time, by the fact that an eccentric rotation motion of eccentricpart 420 is transmitted to piston 421 through connecting rod 422, piston421 performs a reciprocating motion in compression chamber 411.

Following upon the reciprocating motion of piston 421, refrigerant 409in hermetic container 401 is sucked into compression chamber 411 fromsuction muffler 416, and refrigerant 409 of a low pressure flows intohermetic container 401 from the cooling system (not shown in thedrawing) while passing through suction pipe 403. Refrigerant 409 havingbeen sucked into compression chamber 411 is compressed by a motion ofpiston 421, and exhausted into discharge chamber 427 of head 415 viadischarge valve device 414 of valve plate 413. Additionally, refrigerant409 gas of a high pressure having been exhausted into discharge chamber427 of head 415 is exhausted to the cooling system (not shown in thedrawing) from discharge pipe 402.

At this time, the discharge valve device 414 performs such apredetermined opening/closing operation that, by the fact that dischargereed 425 opens, compression chamber 411 and discharge chamber 427 ofhead 415 are communicated through discharge hole 423 and, by the factthat discharge reed 425 closes, the communication between compressionchamber 411 and discharge chamber 427 of head 415 is interrupted.However, in the above conventional constitution, discharge reed 425 canobtain only a constant spring characteristic until it touches stopper428.

Here, about an operation of discharge valve device 414 is discussed inmore detail. When discharge reed 425 of discharge valve device 414opens, if a pressure difference between an inside of cylinder 410 and aninside of discharge chamber 427 of head 415 becomes large,opening/closing part 426 of discharge reed 425 is pushed up bycompressed refrigerant 409 gas of the high pressure, it touches stopper428.

Further, if the pressure difference between the inside of cylinder 410and the inside of discharge chamber 427 of head 415 becomes small,opening/closing part 426 of discharge reed 425 separates from stopper428 by a restoring force of an elastic deformation, thereby closingvalve seat part 424.

That is, a spring characteristic of discharge reed 425, until it touchesstopper 428, shows the constant spring characteristic having noinflection point as shown in FIG. 17. As a result, if the springcharacteristic of discharge reed 425 is weakened, there is obtained thedegree of opening of discharge reed 425 until it touches stopper 428,which has corresponded to a gas flow rate, by the constant springcharacteristic, so that discharge reed 425 is easy to open, and it ispossible to reduce an excessive compression. However, a speed whendischarge reed 425 closes becomes slow and thus a delay in closingoccurs, refrigerant 409 of the high pressure flows reversely incompression chamber 411, and a substantial displacement volume of piston421 becomes small, so that a refrigerating ability lowers.

On the other hand, in a case where the spring characteristic ofdischarge reed 425 has been strengthened, reversely although dischargereed 425 is easy to close, it has a problem that a spring force whenopening ascends and the excessive compression increases.

DISCLOSURE OF THE INVENTION

The hermetic compressor of the present invention is one in which thestopper is provided, in a position corresponding to a movable endvicinity of the discharge reed, with a first regulation part having apredetermined clearance from the movable end vicinity of the dischargereed, and can have such a two-stage spring characteristic that, untilthe movable end vicinity of the discharge reed touches the firstregulation part, the spring characteristic is weak and, after the touch,the spring characteristic is strong.

By the constitution like this, since it is possible to have thetwo-stage spring characteristic, there is obtained the discharge valvedevice which is easy to open and whose closing speed is rapid, so thatit is possible to provide a hermetic compressor in which the excessivecompression is small, whose refrigerating ability is high, and in whichthe energy efficiency is high.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a sectional view of a hermetic compressor in an embodiment 1of the present invention.

FIG. 2 is a plan view of the hermetic compressor in the embodiment 1 ofthe present invention.

FIG. 3 is an exploded view of a discharge valve device in the embodiment1 of the present invention.

FIG. 4 is a side sectional view at a medium-term open time of thedischarge valve device in the embodiment 1 of the present invention.

FIG. 5 is a side sectional view at a terminal open time of the dischargevalve device in the embodiment 1 of the present invention.

FIG. 6 is a spring characteristic diagram of the discharge valve devicein the embodiment 1 of the present invention.

FIG. 7 is a sectional view of a hermetic compressor in an embodiment 2of the present invention.

FIG. 8 is a plan view of the hermetic compressor in the embodiment 2 ofthe present invention.

FIG. 9 is an exploded view of a discharge valve device in the embodiment2 of the present invention.

FIG. 10 is a side sectional view at a medium-term open time of thedischarge valve device in the embodiment 2 of the present invention.

FIG. 11 is a side sectional view at a terminal open time of thedischarge valve device in the embodiment 2 of the present invention.

FIG. 12 is a spring characteristic diagram of the discharge valve devicein the embodiment 2 of the present invention.

FIG. 13 is a sectional view of a conventional hermetic compressor.

FIG. 14 is a plan view of the conventional hermetic compressor.

FIG. 15 is an exploded view of a discharge valve device of theconventional hermetic compressor.

FIG. 16 is a side sectional view of the discharge valve device of theconventional hermetic compressor.

FIG. 17 is a spring characteristic diagram of the discharge valve deviceof the conventional hermetic compressor.

PREFERRED EMBODIMENTS FOR CARRYING OUT THE INVENTION

Hereunder, about embodiments of the present invention, there isexplained by using the drawings.

Embodiment 1

FIG. 1 is a sectional view of a hermetic compressor in an embodiment 1of the present invention, and FIG. 2 is a plan view of the hermeticcompressor in the embodiment 1 of the present invention. Further, FIG. 3is an exploded view of a discharge valve device in the embodiment 1 ofthe present invention, and FIG. 4 is a side sectional view at amedium-term open time of the discharge valve device in the embodiment 1of the present invention. Further, FIG. 5 is a side sectional view at aterminal open time of the discharge valve device in the embodiment 1 ofthe present invention, and FIG. 6 is a spring characteristic diagram ofthe discharge valve device in the embodiment 1 of the present invention.

In FIG. 1, FIG. 2, FIG. 3, FIG. 4, FIG. 5 and FIG. 6, hermetic container101 possesses discharge pipe 102 and suction pipe 103, which areconnected to the cooling system (not shown in the drawing). In a bottompart, oil 104 is stored, and motor element 107, which includes stator105 and rotor 106, and compression mechanism 108 driven by it areaccommodated, and an inside is filled with refrigerant 109. Refrigerant109 is desirably a refrigerant other than a specified flon object havingcorresponded to an environmental issue in recent years, and is R134a orR600a which is a natural refrigerant, or the like.

Next, there is explained about a main constitution of compressionmechanism 108. Cylinder 110 possesses substantially cylindricalcompression chamber 111, and bearing part 112. Valve plate 113 possessesdischarge valve device 114 in a side reverse to cylinder 110, and closescompression chamber 111. Head 116 having formed discharge chamber 115accommodating discharge valve device 114 covers valve plate 113. Suctionmuffler 117 is constituted from tail pipe 118 that is a suction passageof a refrigerant gas, which has been opened into hermetic container 101,and a sound deadening space (not shown in the drawing), and the otherend is communicated into compression chamber 111.

Further, crankshaft 119 has main shaft part 120 and eccentric part 121,and is shaft-supported to bearing part 112 of cylinder 110, and rotor106 is pressing-in fixed. Piston 122 is inserted to cylinder 110 so asto be capable of reciprocating/sliding, and between it and eccentricpart 121 is connected by connecting rod 123.

Next, there is explained about discharge valve device 114 possessed incompression mechanism 108. In valve plate 113, there are provided, in aside reverse to cylinder 110, discharge hole 124 communicating withcylinder 110, and valve seat part 125 having been formed so as tosurround discharge hole 124. Discharge reed 126 consists of a leafspring material, and possesses opening/closing part 129 foropening/closing valve seat part 125.

Stopper 127 regulates the degree of opening of discharge reed 126 andpossesses, in a position corresponding to a movable end vicinity ofdischarge reed 126, first regulation part 132 having provided apredetermined clearance from discharge reed 126. Further, stopper 127possesses, in a position corresponding to opening/closing part 129vicinity of discharge reed 126, second regulation part 133 having aclearance wider than first regulation part 132.

Discharge reed 126 and stopper 127 are disposed in this order, andmonolithically connected and fixed to valve plate 113 by rivet 134.

About the hermetic compressor having been constituted like the above,its operation and action are explained below. If the electricity issupplied to motor element 107, rotor 106 rotates, and crankshaft 119 isrotation-driven. At this time, by the fact that the eccentric rotationmotion of eccentric part 121 is transmitted to piston 122 throughconnecting rod 123, piston 122 performs the reciprocating motion incompression chamber 111.

Following upon the reciprocating motion of piston 122, refrigerant 109in hermetic container 101 is sucked into compression chamber 111 fromsuction muffler 117, and refrigerant 109 of the low pressure flows intohermetic container 101 from the cooling system (not shown in thedrawing) while passing through suction pipe 103. Refrigerant 109 havingbeen sucked into compression chamber 111 is compressed, and exhaustedinto discharge chamber 115 via discharge valve device 114 of valve plate113. Additionally, refrigerant 109 gas of the high pressure having beenexhausted into discharge chamber 115 is exhausted to the cooling system(not shown in the drawing) from discharge pipe 102.

At this time, the discharge valve device 114 performs such anopening/closing operation that, by the fact that discharge reed 126opens, compression chamber 111 inside and head 116 inside arecommunicated through discharge hole 124 and, by the fact that dischargereed 126 closes, the communication between compression chamber 111 andhead 116 is interrupted.

Here, until discharge reed 126 touches first regulation part 132 ofstopper 127, discharge reed 126 opens by a reaction force of refrigerant109 gas of the high pressure. On this occasion, until discharge reed 126touches first regulation part 132 of stopper 127, the constant springcharacteristic having no inflection point is obtained and, by the factthat a first spring constant during this term is made small, the springforce is weakened, thereby making it easy to open.

Next, after discharge reed 126 has touched first regulation part 132 ofstopper 127, since discharge reed 126 additionally bends with a sitetouching first regulation part 132 being made a supporting point, asecond spring constant during this term becomes large in comparison withthe first spring constant. As a result, after touching first regulationpart 132, a strong reaction force of the spring is obtained by a strongspring force and, by the fact that this strong reaction force of thespring acts when discharge reed 126 has entered into its closingprocess, a speed at which discharge reed 126 closes becomes rapid.

Like the above, it is possible to have such a two-stage springcharacteristic that, until the movable end vicinity of the dischargereed 126 touches first regulation part 132, the spring force is weakand, after the touch, the spring force is strong. Accordingly, there isobtained discharge valve device 114 which is easy to open and whoseclosing speed is rapid, so that it is possible to provide the hermeticcompressor in which the excessive compression is small, whoserefrigerating ability is high, and in which the energy efficiency ishigh.

In the embodiment 1, although there has been exemplified one in whichone first regulation part 132 has been provided, by providing thisplurally, it is possible to set a spring characteristic having possesseda more suitable easiness in opening and a more suitable reaction forcein compliance with an opening of discharge reed 126 and, additionally,it is possible to provide the hermetic compressor in which the excessivecompression is small, whose refrigerating ability is high, and in whichthe energy efficiency is high.

After discharge reed 126 has touched first regulation part 132 ofstopper 127, if it opens additionally, it touches second regulation part133. Since second regulation part 133 touches opening/closing part 129vicinity of discharge reed 126, discharge reed 126 is scarcely displacedmore than it. Accordingly, there is suppressed an increase in aninternal stress occurring by a deformation of discharge reed 126, and,even under such a condition that a bending of discharge reed 126 becomeslarge by a liquid compression or the fact that the refrigerant gashaving a high concentration, or the like is compressed, since it ispossible to prevent an extreme increase in a stress of discharge reed126, its breakage can be avoided, so that it is possible to obtain ahigh reliability.

Further, in a case where the liquid compression or the like hasoccurred, a large load is applied to opening/closing part 129 ofdischarge reed 126 by a liquid refrigerant whose density is high, and itis strongly pushed to a touching face of stopper 127. However, sincestopper 127 is fixed to valve plate 113 by rivet 134, there is no factthat stopper 127 is removed, so that it is possible to provide thehermetic compressor whose reliability is high.

When discharge reed 126 touches the touching face of stopper 127,although discharge reed 126 undergoes an impact, in the embodiment 1,there is designed such that the touching face of stopper 127 is workedlike an arc, and a stress of the impact applied to discharge reed 126scarcely affects on a characteristic and a reliability of dischargevalve device 114.

Embodiment 2

FIG. 7 is a sectional view of a hermetic compressor in an embodiment 2of the present invention, and FIG. 8 is a plan view of the hermeticcompressor in the embodiment 2 of the present invention. Further, FIG. 9is an exploded view of a discharge valve device in the embodiment 2 ofthe present invention, and FIG. 10 is a side sectional view at amedium-term open time of the discharge valve device in the embodiment 2of the present invention. Further, FIG. 11 is a side sectional view at aterminal open time of the discharge valve device in the embodiment 2 ofthe present invention, and FIG. 12 is a spring characteristic diagram ofthe discharge valve device in the embodiment 2 of the present invention.

In FIG. 7. FIG. 8, FIG. 9, FIG. 10, FIG. 11 and FIG. 12, hermeticcontainer 201 possesses discharge pipe 202 and suction pipe 203, whichare connected to the cooling system (not shown in the drawing). Hermeticcontainer 201 stores, in its bottom part, oil 204 and accommodates motorelement 207, which includes stator 205 and rotor 206, and compressionmechanism 208 driven by it, and the inside is filled with refrigerant209. Refrigerant 209 is desirably the refrigerant other than thespecified flon object having corresponded to the environmental issue inrecent years, and is R134a or R600a which is the natural refrigerant, orthe like.

Next, there is explained about a main constitution of compressionmechanism 208. Cylinder 210 possesses substantially cylindricalcompression chamber 211, and bearing part 212. Valve plate 213 possessesdischarge valve device 214 in a side reverse to cylinder 210, and closescompression chamber 211. Head 216 having formed discharge chamber 215accommodating discharge valve device 214 covers valve plate 213. Suctionmuffler 217 is constituted from tail pipe 218 that is the suctionpassage of the refrigerant gas, which has been opened into hermeticcontainer 201, and the sound deadening space (not shown in the drawing),and the other end is communicated into compression chamber 211.

Further, crankshaft 219 has main shaft part 220 and eccentric part 221,and is shaft-supported to bearing part 212 of cylinder 210, and rotor206 is pressing-in fixed. Piston 222 is inserted to cylinder 210 so asto be capable of reciprocating/sliding, and between it and eccentricpart 221 is connected by connecting rod 223.

Next, there is explained about discharge valve device 214 possessed incompression mechanism 208. In valve plate 213, there are provided, in aside reverse to cylinder 210, discharge hole 224 communicating withcylinder 210, and valve seat part 225 having been formed so as tosurround discharge hole 224. Discharge reed 226 consists of the leafspring material, and possesses opening/closing part 229 for opening andclosing valve seat part 225.

Stopper 227 regulating the degree of opening of discharge reed 226 isformed monolithically with head 216, and has, in a positioncorresponding to a movable end vicinity of discharge reed 226, firstregulation part 232 having a predetermined clearance from the movableend vicinity of discharge reed 226. Further, it has, in a positioncorresponding to opening/closing part 229, second regulation part 233having a clearance larger than first regulation part 232.

Further, to touching faces of first regulation part 232 and secondregulation part 233 there is fitted cap 234 having been molded fromtetrafluoroethylene which is a solid lubricating material having anoncohesive property and having a refrigerant resistance, a chemicalstability and a heat resistance. Valve plate 213, discharge reed 226 andhead 216 are disposed in this order, and fixed to cylinder 210 side bybolt 235.

About the hermetic compressor having been constituted like the above,its operation and action are explained below. If the electricity issupplied to motor element 207, rotor 206 rotates, and crankshaft 219 isrotation-driven. At this time, by the fact that the eccentric rotationmotion of eccentric part 221 is transmitted to piston 222 throughconnecting rod 223, piston 222 performs the reciprocating motion incompression chamber 211.

Following upon the reciprocating motion of piston 222, refrigerant 209in hermetic container 201 is sucked into compression chamber 211 fromsuction muffler 217, and refrigerant 209 of the low pressure flows intohermetic container 201 from the cooling system (not shown in thedrawing) while passing through suction pipe 203. Refrigerant 209 havingbeen sucked into compression chamber 211 is compressed, and exhaustedinto head 216 via discharge valve device 214 of valve plate 213.Additionally, refrigerant 209 gas of the high pressure having beenexhausted into discharge chamber 215 is exhausted to the cooling system(not shown in the drawing) from discharge pipe 202.

At this time, the discharge valve device 214 performs such anopening/closing operation that, by the fact that discharge reed 226opens, compression chamber 211 inside and head 216 inside arecommunicated through discharge hole 224 and, by the fact that dischargereed 226 closes, the communication between compression chamber 211 andhead 216 is interrupted.

Here, until discharge reed 226 touches first regulation part 232 ofstopper 227, discharge reed 226 opens by the reaction force ofrefrigerant 209 gas of the high pressure. On this occasion, untildischarge reed 226 touches first regulation part 232 of stopper 227, theconstant spring characteristic having no inflection point is obtainedand, by the fact that the first spring constant during this term is madesmall, the spring force is weakened, thereby making it easy to open.

Next, as shown in FIG. 10, after discharge reed 226 has touched firstregulation part 232 of stopper 227, since discharge reed 226additionally bends with a site touching first regulation part 232 beingmade the supporting point, the second spring constant during this termbecomes large in comparison with the first spring constant. As a result,after touching first regulation part 232, the strong reaction force ofthe spring is obtained by the strong spring force and, by the fact thatthis strong reaction force of the spring acts when discharge reed 226has entered into its closing process, the speed at which discharge reed226 closes becomes rapid.

Like the above, since it is possible to have such a two-stage springcharacteristic that, until the movable end vicinity of the dischargereed 226 touches first regulation part 232, the spring force is weakand, after the touch, the spring force is strong, there is obtaineddischarge valve device 214 which is easy to open and whose closing speedis rapid. Accordingly, it is possible to provide the hermetic compressorin which the excessive compression is small, whose refrigerating abilityis high, and in which the energy efficiency is high.

In the embodiment 2, although there has been exemplified one in whichone first regulation part 232 has been provided, by providing thisplurally, it is possible to set the spring characteristic havingpossessed the more suitable easiness in opening and the more suitablereaction force in compliance with the opening of discharge reed 226 and,additionally, it is possible to provide the hermetic compressor in whichthe excessive compression is small, whose refrigerating ability is high,and in which the energy efficiency is high.

As shown in FIG. 11, after discharge reed 226 has touched firstregulation part 232 of stopper 227, if it opens additionally, it touchessecond regulation part 233. Since second regulation part 233 touchesopening/closing part 229 vicinity of discharge reed 226, discharge reed226 is scarcely displaced more than it. Accordingly, there is suppressedthe increase in the internal stress occurring by the deformation ofdischarge reed 226, and, even under such a condition that the bending ofdischarge reed 226 becomes large by the liquid compression or the factthat the refrigerant gas having the high concentration, or the like iscompressed, it is possible to prevent the extreme increase in the stressof discharge reed 226, so that its breakage can be avoided and it ispossible to obtain the high reliability.

In the embodiment 2, stopper 227 and head 216 are monolithically moldedby a die casting and first regulation part 232 and second regulationpart 233 are formed on the same die, so height dimensions of firstregulation part 232 and second regulation part 233 reflect intact a diedimension accuracy. Normally, since the dimension accuracy of the die iscontrolled in several tens micron-meters or less, it is possible toobtain a high dimension accuracy without a necessity to especially workeach face of first regulation part 232 and second regulation part 233,so that it is possible to cause a high production efficiency and astable quality to coexist.

Further, in the embodiment 2, cap 234 is molded from a fluoric resinrepresented by the tetrafluoroethylene.

The tetrafluoroethylene is noncohesive, and possesses an extremely highsolid lubricity. Accordingly, even if cap 234 and discharge reed 226rub, since surfaces mutually slide while scarcely being caught, there issuppressed an abrasion by a metal contact occurring when discharge reed226 touches stopper 227.

Additionally, the tetrafluoroethylene has a noncohesive nature, and thusdischarge reed 226 is easy to be separated from stopper 227, so that itis possible to prevent a delay in closing of discharge reed 226 andincrease the refrigerating ability of the hermetic compressor.

Since the tetrafluoroethylene is high in its vibration damping abilityand has an elasticity, an impact when discharge reed 226 and stopper 227touch is relaxed, a generation of an impact noise is suppressed, andfurther it is possible to prevent a breakage of discharge reed 226 bythe impact, so that it is possible to provide a hermetic compressorwhich is silent and whose reliability is high.

An assembly is only to fit cap 234 having been previously molded by thefluoric resin to stopper 227, so that producibility is good as well.

In the embodiment 2, although the tetrafluoroethylene has been used as asolid lubricating material, even if there is used polybuthylenenaphthalate, polybuthylene terephthalate or polyphenylene-sulfide isused as a resin material having possessed the similar nature, thesimilar action and effect are obtained.

INDUSTRIAL APPLICABILITY

Like the above, since the hermetic compressor concerned with the presentinvention can provide a hermetic compressor in which the delay inclosing is improved and the energy efficiency has been raised, it can beapplied also to uses of an air conditioner, arefrigeration/air-conditioning equipment, and the like.

REFERENCE MARKS IN THE DRAWINGS

110, 210 cylinder

113, 213 valve plate

114, 214 discharge valve device

115, 215 discharge chamber

116, 216 head

122, 222 piston

124, 224 discharge hole

125, 225 valve seat part

126, 226 discharge reed

127, 227 stopper

129, 229 opening/closing part

132, 232 first regulation part

133, 233 second regulation part

1. A hermetic compressor comprising: a cylinder in which a pistonperforms a reciprocating motion; a valve plate sealing an open end ofthe cylinder and having a discharge valve device in a side reverse tothe cylinder; and a head in which a discharge chamber for accommodatingthe discharge valve device is formed, the discharge valve deviceincluding: a discharge hole communicating into the cylinder provided inthe valve plate; a valve seat part formed in a side reverse to thecylinder at the discharge hole; a discharge reed formed of a leaf springmaterial and having an opening/closing part for opening and closing thedischarge hole; and a stopper regulating an opening quantity of thedischarge reed, and including a first regulation part having apredetermined clearance from the discharge reed at a positioncorresponding to a movable end vicinity of the discharge reed.
 2. Thehermetic compressor of claim 1, wherein the stopper includes a secondregulation part having a clearance, which is wider than that of thefirst regulation part, at the position corresponding to theopening/closing part vicinity of the discharge reed.
 3. The hermeticcompressor of claim 1, wherein the discharge reed and the stopper arefixed to the valve plate.
 4. The hermetic compressor of claim 1, whereinthe stopper is molded in the head.
 5. The hermetic compressor of claim2, wherein touching faces of the first regulation part and the secondregulation part are made of a solid lubricating material.